Calculating machine



May 26, 1936. o. J. SUNDSTRAND 2,041,977

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Patented May 26, 1936 CALCULATING MACHINE Oscar J. Sundstrand, Rockford, Ill.,,assignor, by

mesne assignments,

to Underwood Elliott Fisher Company, New York, N. Y., a corporation of Delaware Original application March 3, 1931, Serial N 519,792. Divided and this application November 25, 1932, Serial No. 644,248. In Germany June 5, 1931 38 Claims.

This invention relates to adding and calculating machines, and is a division of my pending application, Serial No. 519,792, filed March 3, 1931, now Patent Number 1,979,295, wherein is provided a totalizer, and a field of value-representing elements arranged in denominational rows or groups, and selectively set by keys or manipulative devices in accordance with the actual amounts, such set elements adapted to control the excursions of totalizer actuators of corresponding denominations which register amounts on the totalizer.

The invention herein set forth relates more particularly to carrying mechanisms suitable to totalizers of various types of machines.

One object is the provision of a novel form of carrying or transfer mechanism for a totalizer, which carrying mechanism includes but few parts, not liable to get out of order, and one wherein the load on the drive mechanism of the machine in connection with which it is used, is so distributed as to render the operation smooth and even. A further object is to provide a novel carrying mechanism which may be readily assembled and disassembled, and of rugged construction to withstand shocks and wear.

In obtaining this result, I have contrived a simple and novel fulcrum common to all of the denominational carrying trains, which enables the ready insertion and removal of any of the carrying units independently of the others.

Still another object is the provision of a novel carrying mechanism which is self-adjusting, in one or another, or both directions of operation.

In attaining these ends, there is provided means to insure the positioning of the carrying pawls and the shifting members associated therewith into their potentially effective positions, the carrying pawls being so formed as to enable the totalizer wheels with which they coact, to restore the pawls and shiftin members to their idle positions during the carrying operations, such restoration being completed by the first-named means, thereby avoiding the necessity for the provision of any special carry-restoring mechanism.

Yet another object is the guidance of the respective carrying pawls in their operation, to maintain them in line with their totalizer wheels for proper operation thereof.

Machines of the travelling totalizer carriage type adapted to effect various mathematical calculations enable the totalizer to be adjusted denominationally in either direction, relatively to the co-related totalizer actuators and the drive means for the carrying mechanisms.

In such machines, it is possible to trip a. carrying mechanism located beyond the sphere of action of the carry driving means of highest value.

An object of this invention is to enable the automatic resetting of such tripped carrying mechanism without attention on the part of the operator and as an incident to shifting the totalizer carriage in either direction, to avoid the possibility of the registration of a wrong total.

The totalizer frame supporting the totalizer wheels is shiftable to engage the wheels with and dis-engage them from their actuators, such shiftllig also affecting the relation of the totalizer wheels to their denominational carrying mechanisms. Switch elements shift back and forth with, and are actuated by, their respective totalizer wheels in either position of the totalizer frame relatively to the carrying mechanisms, and novel means is provided to enable the switch elements to retain control of their respective carrying mechanisms in either shifted position of the totalizer frame.

To these and other ends, this invention includes certain novel features and combinations of parts, all of which will be referred to in greater detail hereinafter and particularly pointed out in the claims.

In the accompanying drawings forming a part of this application:

Fig. 1 is a vertical sectional view longitudinally of the machine from front to rear, showing the application of a carrying mechanism constructed in accordance with my invention to one form of calculating machine;

Fig. 2 is a somewhat similar view, showing the positions assumed by the parts at about the end of the first half rotation of the main drive shaft, certain structure being omitted for clearness;

Fig. 3 is a top plan view of a totalizer carriage, showing the totalizer and the relation of the carrying mechanism thereto;

Fig. 4 is a detail cross sectional view through a carrying unit, showing the positions of the parts during the second half of the cycle of operation of the main drive shaft, the carrying pawl being idly projected rearwardly as when no carrying action is contemplated;

Fig. 5 is a detail left side View, partly in section, of one of the totalizer wheels on its shaft;

Fig. 6 is a sectional view through one of the totalizer wheels;

Fig. 7 is an enlarged front view of a fragment of the totalizer mechanism, partly in section, illustrating the carrying mechanism for the totalizer, parts being omitted for clearness;

Fig. 8 is a detail front view of a group of carrying units;

Fig. 9 is a detail cross sectional view from front to rear, through the totalizer and a carrying unit which are illustrated in side elevation, the parts being in their normal positions;

Fig. 10 is a similar view, showing the parts in tripped positions Just prior to the actuation of the carrying pawl to effect registration of the carry on the totalizer wheel of next higher denomination;

Fig. 11 is a detail plan view of one of the beams supporting the carrying mechanism, to illustrate the arrangement of slots and grooves therein, which accommodate various elements of the carrying units;

Fig. 12 is a front edge view of the transmitting member of the carrying mechanism, for tripping the carry;

Fig. 13 is a detail side view thereof;

Fig. 14 is a front edge view of the member which shifts the carrying pawl from idle to effective position;

Fig. 15 is a detail side view thereof, showing the normal relation of the pawl shifting member to the cross beam;

Fig. 16 is a front edge view of the carrying pawl and its driver;

Fig. 17 is a detail side view thereof;

Fig. 18 is a detail perspective view of the yielding latch mounted on the pawl-shifting means;

Fig. 19 is a fragmentary top plan view of the carrying pawl and its driver, and

Fig. 20 is a detail perspective view showing the means for slidingly supporting the front of the totalizer carriage.

Figure 21 is a plan view, partly broken away and with parts eliminated, showing the totalizer carriage and its manual carriage adjusting means;

Figure 22 is a sectional view from front to rear. through Figure 21.

General description That form of the invention herein selected for illustration, embodies a travelling field of valuerepresenting elements, the elements being arranged in parallel denominational rows to form a field, the home position of which field is offset relatively to a series of denominational totalizer wheel actuators.

A series of key-actuated setting members aligned with the first denominational row of value-representing elements at the left enables the operator to set the elements corresponding with the digits of the amount to be registered on the totalizer.

Escapement mechanism controlled by the numeral keys, advances the field of value-representing elements step by step relatively to the denominational series of actuators, to position the set elements successively into the planes of travel of their corresponding actuators, andto bring the rows of denominational elements successively into the paths of the setting members.

The denominational wheels of the totalizer are mounted in a shiftable frame, means being provided to engage the wheels with and disengage them from their actuators at the proper times to enable the actuators to register on the totalizer the amount set up by the keys.

There are a greater number of totalizer wheels than actuators, the rocking totalizer frame in which the wheels are supported being mounted in a carriage shiftable transversely relatively to the actuators by a manually operable step by step feed means, whereby any desired sequence of totalizer wheels may be positioned opposite the series of actuators for operation thereby, the manual carriage feeding means normally engaging the carriage to hold it where adjusted, and being releasable from the carriage to enable the operator to manually shift the carriage through two or more denominational positions at a time.

A group of carry-actuating devices which may be less in number than the number of totalizer actuators provided, drives the respective carry or transfer mechanisms for the second and higher denominations of totalizer wheels, successively, each totalizer wheel except that of lowest denomination in the totalizer carriage, having its individual carry or transfer mechanism.

The carry-actuating devices are adapted to co-act with any grouping of carrying mechanism whose totalizer wheels may be located opposite the actuators.

Since each totalizer wheel controls the carrying mechanism of the next higher wheel for operation, there being a greater number of carrying mechanisms than carry-actuating devices, it is possible that the wheel of highest denomination, in any position of the carriage relatively to the actuators, except that farthest to the right, may trip the carrying mechanism for the next wheel to the left, but the operation of the tripped carrying mechanism will not be completed, owing to the fact that it lies beyond the group of carry actuating devices.

Heretofore, should the totalizer carriage be adjusted to the right relatively to the actuators while the tripped carrying mechanism remains in such condition, the appropriate carry-actuating device, on operation of the machine, would drive the carrying mechanism tripped in the operation of a preceding problem, for example, and

effect the registration of an incorrect result in the instant problem. Therefore, means is provided whereby any tripped carrying mechanism, the operation of which is uncompleted, shall be reset to normal position incident to the shifting of the totalizer carriage denominationally in one, or preferably either, direction.

To facilitate the performanceof multiplication, division and subtraction, the carriage is provided with separate counters, one of which registers the multiplier or the number of items registered, and the other of which registers the quotient.

The stroke of the main drive shaft may be divided substantially into halves. on the first of which the indexing field and its set elements are driven in one direction to advance the actuators, the main drive shaft, on the remaining half stroke, operating to restore the indexing field to the position from which it was rocked, and simultaneously therewith, operating the carry-actuating members.

Since the totalizer is engaged with its actuators at the beginning of the first half of the stroke and is disengaged therefrom at the beginning of the second half stroke, the carry", if any, can continue throughout practically the entire second half stroke, which affords sufiicient time for the continuance of the earning wave clear across the machine, if necessary.

As the main drive shaft completes the last half of its stroke, the indexing field returns to its starting position, such return being accomplished wholly independently of the main drive shaft.

Totalz'zer The totalizer commonly comprises a plurality of totalizer wheels I16 (Figs. l-3, '1, 9, and 10) journaled for independent rotation on a totalizer shaft 255, which is itself supported for rotation at its opposite ends in the cheek pieces 256 of a rocking totalizer frame, comprising such cheek pieces and a tie bar 251 (Figs. 1 and 2, 9 and 10) extending between and rigidly connecting the cheek pieces at points below the totalizer shaft 255.

An ear 258 at the upper rear end of the lefthand cheek piece 256 is pivotally mounted on the reduced left-hand end 259 of a guide'rod 260 mounted in the left-hand side 262 of a totalizer carriage, the guide rod extending between the sides 26I, 262 (Fig. 3) of such totalizer carriage. A similar car 258 at the upper rear end of the right-hand cheek piece 256 is pivoted on a lag screw 263 connecting the right-hand side 26I of the totalizer carriage with the guide rod 260, the pivotal connections of the cheek pieces enabling the rocking frame supporting the totalizer wheels to swing back and forth relatively to the totalizer carriage in the operation of engaging the totalizer wheels with and disengaging them from the actuators I15,

The totalizer shaft 255 projects through arcuate apertures (not shown) in the sides 26I, 262 of the totalizer carriage and. extends some distance beyond the sides of the totalizer carriage, both ends of the shaft being provided with twirlers or finger wheels for use in clearing the totalizer or resetting it to zero.

Totalzzer wheel structure Referring to the totalizer, each wheel includes a circular rim (Figs. 5 and 6) bearing the proper indicia, as a series of equidistant numbers from to 9 extending around the periphery thereof, if the machine is designed for working problems according to the decimal system.

The inner periphery of the rim carries an annular flange 265, located near one edge of the rim and mounted upon a peripheral shoulder 265 of a disk 261, the hub 268 of which is journaled on the totalizer shaft 255.

The right-hand face of the disk 26? may lie flush with the right-hand edge of the rim, the left-hand edge of the rim extending past the plane of the left-hand face of the disk body 261 and co-acting with the left-hand end of the hub 268 to form an annular chamber housing a correspondingly shaped coiled spring 265. A friction latch, as a stud 210 (Fig. passes through a radial aperture in the left end of the hub 268, the spring 269 pressing against the head or outer end of the stud to yieldingly hold the inner pointed end of the stud in any one of a number of equidistant seats 21I formed about the periphery of the totalizer shaft 255.

The number of seats corresponds with the number of cardinal integers, arranged equidistantly around the rim of the wheel; in this instance, ten, the seats lying in the same radial 5 lines with the cardinal integers on the rim of the wheel. A plurality of friction studs 210 may be employed, as indicated in Fig. 5.

A retaining ring 212 mounted on the extreme left-hand end of the hub cooperates with the disk 261 to hold the annular spring against lateral displacement.

I preferably form separate denominational rows of seats 21I for the inner ends of the friction latches 210 of each totalizer wheel, the ends of which seats merge into the peripheral face of the shaft, as shown in Fig. 6. The annular springs 269 press the latches into the deepest parts of the seats, which tends to prevent shifting of the wheels axially of the shaft. A spacing collar 219 (Fig. 3) on the totalizer shaft 255, between the right-hand cheek piece 256 and the units wheel, and a bracket 280 projecting upwardly from the tie bar 251 and hooking over the totalizer shaft 255 in contact with the lefthand end of the hub 268 of the wheel of highest denomination, positively maintain the wheels against axial movement and retain the pinions 213 thereof in line with the intermediate gears 214.

The ten-toothed pinions 213 (see also Figs. 1, 2, 3, 9 and 10) are mounted on the reduced right-hand ends of the respective wheel hubs 258, and are in constant mesh with the corresponding intermediate gears 214 of a series of gears journaled on a cross rod 215 seated in a longitudinally extending groove 216 (Figs. 9 and 10) formed in the upper edge of the tie bar 251,

such bar being transversely slitted along its upper edge, as at 211, to accommodate the respective intermediate gears and hold them in spaced relation, the slits intersecting the groove 216.

The ends of the cross rod 215 are rigidly mounted in the opposite cheek pieces 256 of the totalizer frame, and fastening means 218 passing through the cross rod and into the tie bar 251, may be provided to secure the cross rod in place.

Totalizer engaging and disengaging mechanism The intermediate gears 214 are automatically engaged with and disengaged from the actuators H5 at the proper times, at each operation of the 4 machine, under control of the main drive shaft 256, by means not herein shown, but fully disclosed in the parent application, heretofore referred to.

The main drive shaft, as it starts its cycle,

the intermediate gears 214 in mesh with the actuators I15 throughout the first half cycle of the main drive shaft to enable the actuators, which advance according to the amount represented by the set value-representing elements 11, to turn their corresponding intermediate ears and totalizer wheels I16 to register such amount there- During the first increment of movement of the second half-cycle of rotation of the main drive shaft, it ceases to act upon the swinging totalizer frame, which thereupon restores to its normal position, and by so doing, disengages the intermediate gears and totalizer wheels from the actuators.

Suitable totalizer aligning and actuator-detaining means are provided to correctly position the totalizer wheels and to prevent premature movement of the actuators during the disengagement of the intermediate gears therefrom.

Carrying mechanism In adding and calculating machines, the carry or transfer mechanism for transferring one to the totalizer wheel of next higher order as often as the capacity of the wheel of next lower order is exceeded, constitutes an important feature.

The mechanism utilized in the present invention to perform this result is of the independent actuator type, simply and strongly designed for accurate and certain operation, and not likely to get out of order.

An important feature of this invention is that the rocking frame supporting the totalizer wheels has been relieved of the weight of the carrying mechanism, which reduces the load on the main drive shaft. The carrying mechanism is mounted in the totalizer carriage and the totalizer frame oscillates between the actuators and the carrying mechanism to bring the totalizer alternately into effective relation with these operating mechanisms.

To this end, each carrying unit includes a normally ineffective transfer pawl operable upon the wheel of higher denomination, a combined guide and positioning means for the transfer pawl, a switch member controlled by the wheel of next lower order, and a transmitting element actuated by the switch member and operable upon the means which guides the transfer pawl to cause it to shift the pawl to effective position.

Corelated therewith are means to releasably retain the pawl-guiding means in either of the positions to which it may be shifted, and means to successively operate or drive the transfer pawls from the lowest to the highest denomination.

The pawl guide is pivotally supported in a novel manner, and ways retain the guide in its predetermined path of travel.

Also the pawl guide, transmitting member, and switch member of each denominational carrying device are assembled for relative movement.

In operation, the wheel of higher denomination automatically restores the transfer pawl to its normal ineffective position as the pawl advances such wheel, and in so doing, resets the pawl guide, together with the floating transmitting member and the switch member to their normal positions preparatory to the next carrying operation.

Referring to the drawings, (Figs. 1, 2, 3, 7-19), it will be seen that the carrying mechanism is mounted on the totalizer carriage just in advance of the totalizer wheels i16, there being, as usual, a carrying unit for each totalizer wheel except that of lowest denomination, which effects the carry" on the wheel of next higher denomination, the carrying units being similar in construction.

A forwardly tilted brace bar 315 (Figs. 1, 2, 4, 9 and 10) extends across the totalizer carriage directly in advance of the totalizer wheels 116, its ends being supported in the opposite sides 26I and 262 of the totalizer carriage.

For convenience of manufacture and assembly, the brace bar is preferably made of two pieces, as indicated by the cross-sectioning, but it will be referred to as a single bar. Spaced in front of and at a somewhat lower plane than the brace bar 3l5, is located a transverse rail 3l8, angular in cross section and having its ends also mounted in the sides 26l and 262 of the totalizer carriage. The rail 3I6, as a whole, lies parallel with the brace bar 315, one flange of the rail lying at right angles to the overhanging forward face of the brace bar.

A rearwardly inclined beam 311 located vertically below the brace bar 315 and at right angles thereto, extends between the sides "I, 252

of the totalizer carriage to which its opposite ends are secured.

The brace bar, rail and beam occupy a somewhat triangular relation and support between them the transfer pawls, the individual guide and positioning members for the pawls, and the transmitting members through which the pawls are brought to their effective positions.

The upper rearwardly inclined face of the beam 3|1, as best shown in Fig. 11, is longitudinally grooved, as at 3l8, to form a seat for a cross rod 313 (Figs. 7-10) suitably secured therein against movement and having its ends projecting into apertures formed in the opposite sides 261, 262 of the totalizer carriage.

Transverse slots 320 (see Fig. 17) along the lower edge of the beam 311 intersect the groove 318 in the beam and accommodate transfer pawlsupporting bell cranks 321 journaled intermediate their ends on the cross rod 319. The upper arms of the bell cranks terminate in fingers 322 (Figs. 9, 10 and 4) overlying the rear edge of the rail MS, with which such fingers normally contact to limit the counter-clockwise travel of the bell cranks under the influence of their restoring springs 323. The outer ends of the springs 323 are anchored to spaced lips 32! struck up from the lower projecting edge of a cover plate 325 superposed upon and secured to the inclined front face of the beam, the upper edge of the cover plate being slotted, as shown in Figs. 1, 2, '7, 9 and 10 to correspond with the slots 320 in the lower edge of the beam, for the purpose of affording clearance for the carrying trains.

3.) Transfer pawls 326 pivoted at their forward ends at 321 to the upper arms of the respective bell cranks 321, extend upwardly and rearwardly through transverse slots 328 (see Figs. 9, l and 4) formed in the lower edge of the brace bar 315, into proximity to the pinions 213 of the totalizer wheels I16. The free ends of the pawls terminate in heads having an abrupt work ing face 329 (Figs. 4, 9, and 1'?) adapted to press against the flank of a tooth of the pinion 213 to advance its corresponding totalizer wheel I16 one step, the lower edge of the head being chamfered as at 330, to form a camming surface against which the succeeding tooth of the pinion operates as the working face 329 presses against the preceding tooth, for a purpose soon to be explained.

Normally, the restoring springs 323 maintain the transfer pawls 326 withdrawn from the pinions 213 to prevent interference therewith as the latter are turned by the actuators I15, or are reset to zero.

The lower arms of the transfer pawl-carrying bell cranks 32l project below the beam 311 into the orbits of a series of radial cams 331, 332 (Figs. 1 and 2) spirally arranged about, and turning with, the main shaft 206, whereby the cams successively contact the respective bell cranks 321 of progressively higher denominations, or anti-friction rolls 333 thereon, to actuate the transfer pawls 32! from lowest to highest denomination, one after the other in regular order. The series of radial cams 33l, 332 extend only part way round the main drive shaft, so as to become effective only after the disengagement of the totalizer wheels and actuators. During the second half cycle of each operation of the machine, the radial cams 331, 332 rock the bell cranks 32l clockwise to cause them to project their transfer pawls 326 rearwardly towards the totalizer pinions 213, and to prevent such action from eifecting an undesired advance of the totalizer wheels when no carrying action is required, there is provided a series of guide and positioning members 334, one for each transfer pawl, such members each comprising a rocking plate of an irregular rectangular shape, arranged closely adjacent its transfer pawl 326 and supported between the brace bar 3I5 and the rail 3I6 at right angles thereto.

The guide and positioning members 334, near what may be termed their upper forward corners (Figs. 9, 10, 15, 14 and 4) are each provided with an undercut or dove-tailed recess 335 to embrace and pivot upon the rear edge of the angular rail 3I6, the opposed overhanging. forward face of the brace bar 3l5 being transversely grooved, as at 336, to form ways in which the irregularly contoured rear edges of the respective guide and positioning members are accommodated, to maintain the guide members in their vertical planes.

A pair of spaced studs or projections 331 extending laterally from the left side of each guide and positioning member 334 embrace the neck of the transfer pawl 326 with which the member is associated, to control the position of the latter relatively to its totalizer pinion 213 and to guide the pawl in its reciprocation.

The upper edge of each guide plate 334 is slotted as at 338 (Figs. 9, 10, 15 and 4), to form a rearwardly extending pilot 339, on which a cylindrical latch 340 is rotatably mounted. Each latch is formed with an axially-extending, round bore to accommodate its pilot and enable the latch to slide back and forth thereon. The latch is also provided with a peripheral longitudinally-extending groove 354 (Fig. 18). The rear end of each latch is oppositely beveled, as at MI, and a spring 342, encircling the pilot 339 between the abrupt front end of the latch 340 and the end wall of the slot 338 in the plate 334, yieldingly forces the beveled end of the latch towards the free end of the pilot and against an opposed beveled rib 343 extending longitudinally of the overhanging face of the brace bar 3l5. The transverse guide ways 336 for the rear edges of the plates extend through the beveled rib 343 to accommodate the free ends of the several pilots 339.

A recess 344 in one wall of the slot 338 facilitates the assembly of the latch and spring on the pilot, the latch 340 being rotatable on the pilot 339 for assembly and disassembly when manually pushed back against the tension of its spring 342 into register with the offset 344 to disengage the groove 354 (Fig. 18) from the rear wall of the slot 338, over which the groove in the latch normally fits, as shown in Figs. 9, l0 and 4, to normally prevent rotation of the latch on its pilot.

The foregoing construction enables each of the guide and positioning members 334 with their guide studs 331, to have a limited rocking movement on the rear edge of the angular rail 3I6, as a fulcrum, the spring-pressed latches 340 operating to hold the guide and positioning members 334 in their upper positions, when the lower bevels of the latches lie in contact with the upper bevel of the rib 343, at which time, the studs 331 hold the transfer pawls 326 at such an angle rela tively to their totalizer pinions 213 that the pawls, on their reciprocation, pass over the teeth of the pinions without contacting therewith, as shown in Fig. 4, wherein the transfer pawl is illustrated at the rearmost end of its travel.

However, when a totalizer wheel I16 of lower order has been rotated by its actuator I15 to such extent that upon the next step of movement the capacity of the wheel will be exceeded, it is necessary to arrange for the addition of 1 on the wheel of next higher order on that operation during which the capacity of the wheel is exceeded.

To accomplish this result, the totalizer pinions 213 of the totalizer wheels, are each rovided with a trip finger 345 (Figs. 6, 7, 9 and 10) comprising, in the present instance, a lateral extension from one of the teeth of the pinion, adapted, as the wheel passes from its "9" to its 0 position at the reading line, to wipe over the inclined face of a cam 346, best shown in Figs. 9 and 10, carried on a switch member or arm 341, one of which is journaled by one end on the cross shaft 215 alongside each of the intermediate gears 214.

The free end of each switch member 341 rests loosely upon an extension 348 (Figs. 9, 10, 13 and 12) projecting to the right from a transmitting member or slide 349 shiftably mounted in a groove 350 (Figs. 11 and 13) formed transversely of the upper inclined face of the beam 3 I1, adjacent the guide and positioning member 334 to the left of the totalizer wheel of lower order.

The transmitting members 349 correspond in number with the number of switch members 341, and lie to the left of their respective guide and positioning members 334 (see Figs. 7 and 8) to enable the extensions 348 of such transmitting members to overlie and contact with inclined tails 35I (Figs. 9, 10 and 15) projecting rearwardly from what may be termed the lower right-hand corners of their associated guide and positioning members or plates 334, which tails occupy inclined slits 352 formed in the upper rear corner of the beam 3I1.

These transmitting members are recessed, as at 353, (Figs. 9, 10 and 13) to afford a clearance for the cross rod 3I9, the cover plate 325 operating to retain the transmitting members in their grooves in the cross beam 3I1.

The bottom edges of the switch members 341 ride back and forth on the lateral extensions 348 of their transmitting members 349 as the totalizer frame is rocked to mesh the intermediate gears 214 with, and disengage them from the teeth I89 of the actuators I15 to maintain control of their respective carrying devices in either position of the totalizer frame.

Assume that the parts of the carrying mechanism are in their normal positions (Figs. 1, 2 and 9) wherein the latches 340 contact the upper beveled face of the universal rib 343 to maintain their respective guide and positioning members 334 in their upper positions, so that the pairs of studs 331 hold their reciprocating transfer pawls 326 at such angles to the totalizer pinions 213 that the pawls, as they thrust rearward-' ly (Fig. 4) escape the latter. The lateral extensions 348 of the transmitting members or slides 349 lie over and in contact with the tails 35I of their respective guide and positioning members 334, and the free ends of the switch members 341 rest upon the rear faces of such extensions. It will be clear that a trip finger 345 will wipe over the cam 346 of its co-related switch memher, as the corresponding totalizer wheel driven by its actuator I15, passes from 9 to 0" during the first half cycle of operation of the main drive shaft 286, to rock the switch member counter-clockwise from the position shown in Fig. 9 to that shown in Fig. 10.

During such counter-clockwise travel, the switch member 341 presses against the extension 343 of the transmitting member 343 to drive the transmitting member downwardly in its groove 350. The lateral extension 343, in turn, presses against the tail 35l of its associated guide and positioning member 334 located opposite the pinion 213 of the totalizer wheel of next higher denomination, and rocks the guide and positioning member clockwise, which, by reason of the control of the studs 331 over the transfer pawl 326, swings the pawl downwardly into line with the pinion of such totalizer of higher order, as shown in Fig. 10.

The throw of the guide and positioning member 334 and the transfer pawl 326 in clockwise direction may be limited by contact of the rear edge of the member 334 against the bottom of the groove 336 in the brace bar 3I5.

As the guide and positioning member rocks clockwise, the beveled latch 340 rides over the high point of the beveled rib 343, compressing the spring 342, which forces the latch outwardly again as the latch comes opposite the lower beveled face of the rib to assist in switching the guide and positioning plate clockwise in case of lost motion between the transmitting member 349 and the plate 334, and to yieldingly retain the parts in the positions to which they have been adjusted.

The parts remain in such adjusted positions during the remainder of the first half cycle of the main drive shaft 236, and at about the time when the drive shaft 206 completes the first step of the second half cycle, to enable the disengagement of the totalizer from the actuators, it causes the right-hand transfer cam 33 (Figs. 1 and 2) to wipe past the corresponding pawl-carrying bell crank 32l, rocking the latter clockwise against the tension of its spring 323 to impart a rearward thrust to the associated transfer pawl 326, the remaining transfer cams 33l, 332 operating their respective pawl-carrying bell cranks in close succession as the main drive shaft completes its second half cycle.

Such transfer pawls as are maintained by their guide and positioning members 334 in normal ineffective positions (Fig. 9) merely thrust rearward idly, and are retracted together with their bell cranks MI, by the springs 323, after the transfer cams escape past the pawl-carrying bell cranks.

In this connection, it will be noted that the shape of the transfer cams 33!, 332 is such as to retain control of the pawl-carrying bell cranks 32l during their return to normal position under the influence of their springs 323 whereby to reduce the noise hitherto incident to such return.

Where a guide and positioning member 334 has been adjusted by the totalizer pinion 213 of lower order, to locate its transfer pawl 326 in line with the totalizer pinion of next higher order, however, the abrupt face 329 of such pawl, on the rearward thrust, strikes the opposed tooth of its pinion and turns the pinion one step in advancing direction.

As the pinion of higher denomination turns under the action of the abrupt face of the head of the pawl against that tooth which is in its path of travel, the succeeding tooth of the pinion contacts the obtuse cam face 330 of the pawl and crowds the pawl upwardly towards or to its normal idle position, thereby shifting the abrupt face 329 of the pawl out of contact with the tooth against which it was operating. Obviously, the extent of such abrupt face and the relation be tween it and the cam face 330 must be such that the pawl can advance the totalizer pinion a sumcient distance before the abrupt face 323 loses contact with its tooth.

As the pawl 326 is rocked-upwardly towards its normal idle position, it, in turn, rocks the guide and positioning member 334 counter-clockwise because of its contact with the uppermost of the guide studs 331.

The cam face 33!! need not be of such extent as to require the succeeding tooth of the pinion to completely restore the pawl 326 and positioning member 334 to their normal idle positions, it being necessary merely for the succeeding tooth to rock the pawl and guide member counterclockwise (Fig. 10) until the spring-pressed latch 343 crosses the apex of the rib 343, whereupon the pressure of the spring 342 against the latch causes its lower beveled face to ride rearwardly along the upper beveled face of the rib and complete the return of the guide and positioning member and its pawl to their normal positions.

The same action may occur in shifting the guide and positioning member and pawl to their effective positions, it being merely necessary for the trip finger 345 to depress the switch member 341 and transmitting member 343 and rock the guide and positioning member 334 and its pawl clockwise until the latch 340 passes below the apex of the rib 343, whereupon the spring 342 operating upon the latch as above explained, will cause the completion of the movement of the guide and positioning member and its pawl to effective position relatively to its totalizer pinion.

By arranging for the successive operation of the carrying units from lowestto highest denomination, the familiar carry upon a carry cannot be lost, but is effected at the proper time.

The arrangement whereby the return of the indexing carriage 13 to its starting position preparatory to the entry of a new amount therein is effected by motors independently of the main drive shaft, as set forth in the parent application Serial No. 519,792, filed March 3, 1931, enables the division of the time of operation of the main drive shaft into two half cycles, the first of which is utilized to engage the totalizer and actuators and enter the amount on the totalizers, and the second of which is utilized to disengage the totalizer and actuators and effect transfers on the totalizer wheels.

The provision whereby the return of the index carriage to the right occurs independently of the operation of the main drive shaft, which return may continue after the end of the operation of the main drive shaft, as also explained in the parent application above-mentioned, renders unnecessary the provision of a definite phase of the movement of the main drive shaft to effect such carriage return, and thus enables the use of substantially the entire second half cycle of operation of the main drive shaft to effect the carrying operation, which insures accuracy and avoids the imposition of sudden strains on the carrying mechanism.

Totalizer carriage To facilitate the performance of multiplication, and division, as well as to extend the use of the machine in adding and complementary subtraction operations, the totalizer carriage, heretofore briefly referred to, is arranged for adjustment across the machine, and is equipped with a larger number of totalizer wheels I16 than is usually provided for commercial additions, there being twenty such totalizer wheels in the present instance, though more or less might be used without departure from the spirit and scope of the invention.

It has been stated, heretofore, that the totalizer carriage includes the right and left side frames 26I, 262 (Fig. 3) united by the cross rod 268, serving as a center about which the totalizer frame rocks, and by the brace bar 3I5, angular rail 3I6 and beam 3I'I. The totalizer carriage furthermore includes a supporting rail 388 ex tending between and secured at its ends to the front ends of the totalizer carriage side frames 28I, 262, respectively, the supporting rail intermediate its ends being slidingly mounted for iongitudinal travel in ways 38I (Fig. 20) formed in the head 382 at the rear end of a sleeve 383 extending horizontally fore and aft of the machine.

and carried on the upper end of a pillar 384, (Figures 21 and 22) projecting upwardly from the baseof the machine, all as fully set forth in the parent application, Serial No. 519,792, above mentioned.

The supporting cross rod 288 connecting the rear ends of the side frames 26I, 282 of the totalizer carriage frame is mounted for longitudinal movement in the forwardly projecting ends of brackets 385, (Figs. 1, 2, and 7), the rear ends of which are respectively fastened to upstanding portions of the left side frame 52 and a partition plate (not shown) of the machine. A tie bar 319 connects the brackets 385 to impart rigidity thereto.

This method of supporting the totalizer carriage enables it to be shifted in either direction laterally of the machine to position any group of totalizer wheels opposite the groups of actuators I15 for operation thereby.

In simple adding operations, this adjustability of the carriage relatively to the actuators enables the operator, in effect, to divide the series of totalizers into two or more groups and to add a corresponding number of. rows of amounts separately, so long as the added amounts in the group of totalizer wheels to the right do not extend into the next group of wheels to the left. However, the plurality of totalizer wheels is more particularly adapted for the performance of subtraction and division, or in multiplying large amounts.

As a convenient means enabling the operator to feed the totalizer carriage in either direction, the sleeve 383 (Figs. 22 and 20) is longitudinally bored to accommodate a spindle 386, the inner end of which carries a barrel 381 rotatable in a similarly shaped chamber 388 formed in the head 382 of the sleeve and communicating with the space formed between the ways 38I in the head.

The barrel is of greater diameter than the height of the supporting rail 388, and carries one or more rearwardly projecting driving teeth 389 adapted to co-act with teeth or serrations 398 formed in the front face of the rail 388. A finger piece 39I (Figs. 1-3) on the outer end of the spindle 386 which projects forwardly beyond the forward end of the sleeve 383, facilitates rotation of the spindle in either direction to enable the teeth 389 to engage the teeth 398 of the totalizer carriage supporting rail 388 and shift the carriage step by step to the right or left, as desired, in adjusting the totalizer relatively to the group of actuators.

An arresting stop 558 is located between the teeth or serrations 398 of the rack formed on the front face of the rail 388, near the opposite ends of such rack, to limit the feed of the totalizer carriage in opposite directions by preventing the passage of the driving teeth 389 between the teeth of the rack when the carriage has arrived at either predetermined limit of its travel.

Normally the driving teeth 389 remainin engagement with the teeth 398 of the supporting rail to prevent accidental shifting of the totalizer carriage out of its adjusted position, but as one means to allow the operator to shift'the totalizer through distances greater than a single step at a time, the chamber 388 is of sufficient length to enable the operator, by an endwise pull on the handle or finger piece 39 I, to withdraw the barrel 381 and its teeth 389. into the chamber and out of engagement with the teeth 398 of the supporting rail 388, thereby freeing the totalizer carriage for adjustment freely in either direction directly to any point in its path of travel.

A spring 392 seated in a recess (Figs. 20 and 22) formed above and parallel with the bore of the spindle 386 and communicating with the chamber 388, forces a detent pin 393 reawardly against the forward face of the barrel 381, the detent pin being forced farther into the spring seat or recess and storing greater tension in the spring 392 when the operator draws the spindle and barrel forwardly.

Upon release of the handle or finger piece 39I after the operator has manually positioned the carriage as desired, the spring 392 forces the detent pin against the barrel to thrust the latter with its spindle and driving teeth 389 rearwardly, to re-engage the driving teeth with the teeth or serrations 398 on the carriage supporting rail 388 and hold the carriage where adjusted.

Conveniently, the inner end of the detent pin 393 contacts one or another of a plurality of opposed cam faces 394 formed on the front end of the cylindrical barrel 381 in such relation with the driving teeth 389 that when the rear end of the detent pin lies at the low point of a cam 394, the driving teeth will lie between the teeth 398 of the opposed carriage supporting rail 388 to lock the carriage against longitudinal movement, the barrel with its teeth thus constituting a combined locking and feeding head for the totalizer carriage.

To use the totalizer for the purpose of carrying two or more separate accumulations of items simultaneously, it is merely necessary for the operator to be careful to allow a suilicient spacing between the items entered in the separate accumulations. Thus, assume it is desired to add two series of items simultaneously, no single item being over four figures, for instance, as in the following example:

The operator will position the totalizer carriage by means of the manually operable handle 39I, as far to the right as possible. This will locate the tenth, eleventh, twelfth, etc. to the nineteenth adding wheels I16 opposite the ten adding racks I15.

The operator will now set up the first item of the left hand column of figures, and operate the machine to enter the item on the tenth, eleventh, twelfth, and thirteenth adding wheels I16, the remaining wheels to the left of the thirteenth adding wheel affording plenty of room for the carry-overs from the thirteenth wheel, or even the direct addition of items of more than four figures.

After entering the first item 4987 in the left hand column of the example, the operator may continue to successively enter the remaining items in the left hand column without shifting the totalizer carriage until after the entry of the last figure, or he may operate the handle 39l immediately after the entry of the first item, to shift the carriage to its extreme left hand position, wherein the first ten adding wheels H6 at the right will be in association with the ten adding racks I15, whereupon the first item of the right hand column of the example may be entered on the first four adding wheels, there being five adding wheels intervening between the fourth and the tenth, on which the carry-overs from the fourth wheel may be accumulated.

If care is taken to avoid the accumulation of an amount on the right hand adding wheels which will extend onto the tenth or higher wheels of the totalizer, in the example given, two totals may be simultaneously carried on a twentywheel totalizer. Of course, when dealing with items of but two or three figures, a larger number of totals may be simultaneously carried in spaced relation on a totalizer of the above-mentioned capacity.

Restoration of incomplete carry Reference has been made to the fact that the carrying mechanism controlled by whichever totalizer wheel is next above that wheel of highest denomination in any particular adjustment of the totalizer carriage, except when the carriage is in its farthest position to the right, may be shifted to operative position, but will not be operated because its pawl-carrying lever 32l (Figs. 1, 2 and 7-10) lies beyond and to the left of the pawl-actuating cam 332 of highest denomination.

Obviously, adjustment of the totalizer carriage towards the right from its extreme left-hand position would bring such effectively-positioned carrying mechanism within the scope of operation of one or another of the carry-actuating cams 33i, 332, depending upon the extent of such adjustment, and if no precaution were taken to prevent, an operation of the main drive shaft 206 with the totalizer carriage in its newly adjusted position, would result in a completion of the carry and the unintentional addition of 1" on a totalizer wheel, which would render erroneous the result of a new, that is, succeeding calculation. To prevent the possibility of such objectionable occurrence, there is provided means automatically effective whenever the totalizer carriage is shifted in either direction, to reset any shifted or tripped carrying mechanism to its normal ineffective position, one form of which means is as follows:

It will be remembered that the tails 35! (Figs. 4, 9, and at the rear lower corners of the guide and positioning plates 334 are accommodated in parallel guide slots 352 formed at an incline in the cross beam 3", which are in register with recesses 355 (Figs. 7, 9 and 10) formed in the rear edge of the cover plate 325.

A carry restoring bar 490 rests upon the upper face of, and lies parallel with, the cover plate.

Headed studs 49l (Fig. 7), one only being shown, pass through transversely extending slots 492 in the carry-restoring bar 490 near its opposite ends, and into the fixed cover plate 325, the forward edge of the carry-restoring bar having teeth 493 formed therein which lie between the upturned ears 324 at the forward edge of the cover plate, and project therebeyond for guidance.

If desired, springs 4 94 anchored at their opposite ends to the carry-restoring bar and to ears 324 on the cover plate, may be provided to urge the carry-restoring bar forwardly as far as permitted by the rear end walls of the slots 492, to maintain the teeth projected beyond the forward edge of the covertplate 325 which, in turn, overhangs the beam 3I1, as shown in Figs. 9 and 10.

There are, preferably, a sufficient number of teeth 493 to insure the operation of the carryrestoring bar 490 in any adjusted position of the totalizer carriage.

The outer ends of the teeth 493 are oppositely beveled (see Fig. 7) to co-act with the oppositely beveled faces of stationary cams 495 (Figs. 1 and 2), one only being shown, conveniently spaced apart, as by being mounted on the left side frame 52 and the intermediate partition (not shown) so that the upper ends of the stationary cams lie in line with the edges of the teeth 493 when the totalizer carriage is shifted across the machine in either direction, the beveled ends of such restoring cams 495 projecting into the space between those pairs of teeth which lie adjacent thereto in any adjusted position of the carriage.

The rear edge of the carry-restoring bar 490 is recessed, as at 491, the front wall of such recess normally lying transversely across and a little in front of the inclined front edges of the vertically-arranged guide and positioning plates 334 at points adjacent the lower front corners of such plates (see Figs. 1 and 2, 9 and 10).

In the ordinary operation of the machine, the guide and positioning plates 334 rock clockwise and counterclockwise, as heretofore explained, without interference from the carry-restoring bar 490, the forward edges of the guide and positioning plates, when at their clockwise limit, lying in substantial contact with the recessed edge of the carry-restoring bar (Fig. 10), and in the event that the capacity of the totalizer is exceeded, either additively or subtractively, as heretofore explained, the guide and positioning plate 334 controlling the effectiveness of the carrying pawl 326 associated with the totalizer wheel beyond and to the left of the pawl-actuating cam 332 of highest denomination, will be rocked to its clockwise limit of travel by the active totalizer wheel of highest denomination, thereby setting its carrying pawl in position to effect a carry on the wheel to the left of the active totalizer wheel of highest order.

However, in order to drive such set carrying mechanism, it would be necessary to shift the totalizer carriage to the right to bring the pawlcarrying lever 32! associated with the tripped carrying pawl 326, into operative relation with one or another of the pawl-actuating cams 33!, 332, and during the first step of such travel the teeth 493 of the carry-restoring bar 490, which lie adjacent the cams 495, ride over the projecting beveled ends of their associated cams which force the carry-restoring bar rearwardly, causing its recessed rear edge 491 to contact the forward edge of the tripped guide and positioning plate 334 to restore the plate and its carrying pawl 326 to their normal positions, wherein the pawl is ineffective.

Employment of a pair of restoring cams 495 spaced apart as explained, insures an even motion of the carry-restoring bar 490 transversely of the cover plate without canting or binding on the guides 49L After the teeth 493 have escaped past the beveled ends of the restoring cams 495, thesprings 494 may advance the carry-restoring bar to remove its rear edge from the paths of travel of the guide and positioning plates 334 when shifted in the ordinary operation of the machine, or the return springs 323 for the pawl-carrying levers 32l may be relied upon to effect this result.

Obviously, the totalizer carriage, when shifted to the left, will effect the same result, and the carry-restoring bar 490 being common to all the carrying mechanisms, serves to insure the restoration of any tripped carrying mechanism to normal whenever the totalizer carriage is shifted.

Obviously, the tripped guide and positioning member 334, as it is returned to normal by the carry-restoring plate 490, resets its transmission slide 349 and switch member 341 to their normal positions in readiness for operation by the corresponding totalizer wheel H5 in its adjusted relation to the adding racks I15.

Changes may be made in the forms and arrangement of the parts above set forth, and omissions, and substitutions of equivalents made, without departing from the spirit and scope of the invention.

What is claimed as new, is:

1. The combination with a plurality of totalizer wheels; and actuators therefor; of a switch member; means controlled by a wheel of lower order, to shift the switch member; a transmitting element actuated by the switch member; a transfer pawl; a recessed transfer pawl guide to maintain the pawl in ineffective or effective position, and operable by the transmitting element; and a support embraced by the recess to form a fulcrum for the guide.

2. The combination with a plurality of totalizer wheels; and actuators therefor; of a switch member; means controlled by a'wheel of lower order to shift the switch member; a transmitting element actuated by the switch member; a transfer pawl; and a guide to maintain the pawl in either of two positions, the guide having a projection extending into the path of the transmitting element to enable the latter to shift the guide and locate the pawl in one of its positions.

3. The combination with a plurality of totalizcr wheels; and actuators therefor; of a shiftable switch member operable by a wheel of lower order at a predetermined point in its rotation; a transmitting slide located adjacent a wheel of higher order and having a laterally extending lip normally lying in the path of the switch member; a transfer pawl for the wheel of higher order, and having an effective and an ineffective position; means to impart a driving stroke to the pawl; and a shiftable guide for the pawl, having a projection lying in the path of the transmitting slide for operation thereby, to shift the pawl to one of its positions.

4. The combination with a plurality of totalizer wheels; and actuators therefor; of a transfer pawl having an effective and an ineffective position; means to actuate the transfer pawl in one direction; a frame having a way formed therein; and a shiftable pawl guide engaging the pawl to switch the latter to its effective position, the pawl guide operating in one of the ways in the frame.

5. The combination with a plurality of totalizer wheels; and actuators therefor; of a transfer pawl having an effective and an ineffective position; means to actuate the transfer pawl in one direction; a frame having a cam face, and ways formed transversely of the cam face; a pawl guide engaging the pawl, and shiftable in one of the ways to locate the pawl in its effective position; 5 and means on the guide to co-act with the cam face and maintain the guide where adjusted.

6. The combination with actuators; a shiftable totalizer frame; totalizer wheels mounted therein; and means to shift the frame to engage and 10 disengage the totalizer wheels relatively to their actuators; of a support for the totalizer frame, including parallel cross bars; a transfer pawl; means to actuate the transfer pawl in one direction; a pawl guide mounted between the cross 16 bars, the guide being recessed to embrace the edge of and rock upon one of the cross-bars, the opposed cross bar having a way to accommodate the free edge of the guide, the guide adapted to maintain its pawl in effective or ineffective posi- 0 tion relatively to its corresponding wheel; and means controlled by the wheel of lower order to shift the guide to locate the pawl in effective position.

7. The combination with a plurality of total- 25 izer wheels turning about a common center; and actuators therefor; of a switch memb'er rotatable on another center and operable by a wheel of lower order at a predetermined point in its rotation;

a transfer pawl for a wheel of higher order; 30 means to drive the pawl; a guide for the pawl, rotatable about still another center, and adapted to maintain the pawl in effective or ineffective position; and a reciprocatory transmitting element shiftable relatively to and interposed be- 35 tween the switch member and the guide.

8. The combination with a plurality of totalizer wheels and actuators therefor; of a switch member controlled by a wheel of lower order; a transfer pawl for a wheel of higher order; means 40 to drive the pawl; a shiftable guide for the pawl adapted to maintain the pawl in its effective and ineffective positions; a reciprocatory transmitting element interposed between the switch member and the pawl guide; and a track traversed by the transmitting member.

9. The combination with a plurality of totalizer wheels; and actuators therefor; of a switch member operable by a wheel of lower order at a predetermined point in its rotation; a transfer pawl for a wheel of higher order; means to drive the pawl; a shiftable guide for the pawl adapted to maintain the pawl in its effective and ineffective positions; and a reciprocatory transmitting element interposed between the switch member and the pawl guide, and operable by the switch member to switch the guide and locate the pawl in one of its positions, the wheel of higher order operable upon the pawl to restore the guide to the other of its positions, and to return the transmitting element into the path of the switch member.

10. The combination with a group of totalizer wheels; a carrying mechanism therefor, including its rotation and engaging the transmitting member, the totalizer wheel of higher order adapted to restore the positioning member and the transmitting element and switch member to their normal positions.

11. The combination with a group of totalizer wheels; a carrying mechanism therefor, including a transfer element shiitable from its normal ineffective position to its effective position to actuate a totalizer wheel of higher order; and drive means for the transfer element; of a guide and positioning means for the transfer element, normally operative to maintain the transfer element ineffective and shiftable to adjust the transfer element to its effective position; means to retain the guide and positioning means where adjusted; and means interposed between the guide and positioning means, and a totalizer wheel of lower order, and Operable by the wheel at a predetermined point in its rotation, to adjust the guide and positioning means and render the transfer element effective, the totalizer wheel of higher order adapted to restore the guide and positioning means together with the interposed means to their normal positions.

12. The combination with an adjustable totalizer carriage; totalizer wheels mounted therein; actuators for the totalizer wheels; and means to adjust the totalizer carriage and its totalizers relatively to their actuators; of carrying mechanism associated with the totalizer wheels, including transfer pawls, shiftable to effective and ineffective positions relatively to their totalizer wheels; and means actuated by the totalizer carriage, when adjusted relatively to the actuators, to restore to ineffective position any pawl which occupies its effective position relatively to its totalizer wheel.

13. The combination with a series of actuators; a series of totalizer wheels operable by the actuators, and adjustable to co-relate different wheels of the series with the actuators; of carrying mechanism associated with the totalizer wheels, and including transfer elements shiftable to effec tive and ineffective positions; means to drive the transfer elements; and resetting mechanism for any transfer element which lies beyond the zone of operation of the drive means therefor, said resetting mechanism effective incident to the said adjustment of the totalizer wheels relatively to their actuators.

14. The combination with a series of actuators; a series of totalizer wheels operable by the actuators, the actuators and totalizer wheels being relatively adjustable to co-relate different wheels and actuators; of carrying mechanism associated with the totalizer wheels, and including transfer elements shiftable to effective and ineffective positions under control of the totalizer wheels; drive means for the transfer elements, and relatively to which the transfer elements are adjustable incident to the relative adjustment of the actuators and totalizer wheels; and means also operable as an incident to the relative adjustment of the actuators and totalizer wheels, to re set to normal any transfer element beyond the zone of operation of the drive means, which has been set to effective position under the previous relation of actuators and totalizer wheels.

15. The combination with a series of actuators, and a series of totalizer wheels, relatively adjustable to co-relate different totalizer wheels and actuators; of carrying mechanism associated with the totalizer wheels, including transfer elements shiftable to effective position under control of the totalizer wheels; drive means for the transfer elements, and relatively to which the transfer elements are variously positioned incident to the relative adjustment of the totalizer wheels and actuators; a relatively stationary restoring member; and means partaking of said relative adjustment of the totalizer wheels and actuators, and adapted to co-act with the restoring member to reset any transfer element which lies in effective position, as an incident to the said relative adjustment of the totalizer wheels and actuators.

16. The combination with a series of actuators, and a series of totalizer wheels, relatively adjustable to co-relate different totalizer wheels and actuators; of carrying mechanism associated with the totalizer, including transfer elements shiftable to effective position under control of the totalizer wheels; drive means for the transfer elements, and relatively to which the transfer elements are variously positioned incident to the relative adjustment of the totalizer wheels and actuators; a restoring cam member; and resetting means partaking of said relative adjustment between the totalizer wheels and the actuators, and cooperable with the restoring cam member at any point in the travel of the resetting means, to return to normal any transfer element which lies in effective position, as an incident to the initiation of a carrying operation during the previous relation of the totalizer wheels and actuators.

17. The combination with a series of totalizer wheels adjustable as a unit in one plane; and carrying mechanism associated with the totalizer wheels and adjustable therewith, the carrying mechanism including transfer elements shiftable to effective position by the totalizer wheels; of means to drive the transfer elements, and relatively to which the transfer elements are variously positioned upon the said adjustment of the totalizer wheels; and means to restore any transfer element from its effective position to its normal position, as an incident to said adjustment of the totalizer wheels.

18. The combination with a series of totalizer wheels adjustable as a unit in one plane; and carrying mechanism associated with the totalizer wheels, and adjustable therewith, the carrying mechanism, including transfer elements, shift able to effective position by the totalizer wheels; of means to drive the transfer elements, and relatively to which the transfer elements are variously positioned upon said adjustment of the totalizer wheels; a relatively stationary restoring cam; and resetting means adjustable with the totalizer wheels, to contact the restoring cam and return any transfer element from its effective position to its normal position.

19. The combination with a group of totalizer wheels adjustable as a unit; and carrying mechanism associated therewith, the individual elements of which carrying mechanism are shiftable to effective position by the totalizer wheels in computing operations; of means to drive the individual carrying elements, and relatively to which the carrying mechanism is adjusted with the totalizer wheels; a resetting means for those individual carrying elements which lie in effective position when the totalizer wheels are so ad justed; and means to render the resetting means effective.

20. The combination with a group of totalizer wheels adjustable as a unit; and carrying mechanism associated therewith, the individual elements of which carrying mechanism are shiftable to effective position by the totalizer wheels in computing operations; of means to drive the individual carrying elements, and relatively to which the carrying mechanism is adjusted with the totalizer wheels; a resetting means to restore any individual carrying element from its effective to its normal position; and means to render the resetting means effective at any point in the adjustment, as an incident to said adjustment of the totalizer.

21. The combination with a group of totalizer wheels adjustable as a unit; and carrying mechanism associated therewith, the individual elements of which carrying mechanism are shiftable to effective position by the totalizer wheels in computing operations; of means to drive the individual carrying elements, and relatively to which the carrying mechanism is adjusted with the tota izer wheels; atoothed resetting means to restore any individual carrying element from its effective to its normal position; and an operating tooth to co-act with any of the teeth of the resetting means, to effect operation of the resetting means.

22. The combination with a group of totalizer wheels, and carrying mechanism therefor, the wheels and carrying mechanism being adjustable as a unit in opposite directions; the carrying mechanism including individual carrying elements shiftable to effective position under control of the totalizer wheels; of drive means for the carrying mechanism, and relatively to which the carrying mechanism is adjustable with thetotalizer wheels; resetting means for the carrying elements adjustable with the carrying mechanism; and means with which the resetting means cooperates irrespective of the direction of adjustment to restore to normal any carrying element in effective position.

23. The combination with a group of totalizer wheels, and carrying mechanism therefor, the wheels and carrying mechanism being adjustable as a unit; the carrying mechanism including individual carrying elements shiftable out of and into normal position under control of the totalizer wheels; of drive means for the carrying mechanism, and relatively to which the carrying mechanism and totalizer wheels may be adjusted; a resetting member common to the individual carrying elements and adjustable with the carrying mechanism, to restore any carrying element to its normal position incident to the adjustment of the totalizer wheels and carrying mechanism; and means to effect the operation of the resetting member during such adjustment.

24. The combination with a totalizer carriage; a series of totalizer wheels mounted therein; a series of actuators relatively to which the carriage and totalizer wheels are transversely adjustable in either of two directions; and carrying mechanism for the totalizer wheels, including individual transfer elements; of drive means for the transfer elements relatively to which the transfer elements are adjustable; a universal resetting member for the transfer elements mounted for adjustment with the carrying mechanism; and means cooperable with the resetting member in anyof its ad usted positions to actuate the latter incident to its adjustment in either direction.

25. The combination with a totalizer carriage; a series of totalizer wheels mounted therein; a series of actuators relatively to which the carriage and totalizer wheels are transversely adjustable in either of two directions; and carrying mechanism for the totalizer wheels, including individual transfer elements; of drive means for the transfer elements relatively to which the transfer elements are adjustable; a universal resetting bar for the transfer elements adjustable with and slidably mounted on the totalizer carriage; a plurality of spaced cam projections on the resetting bar; and a fixed cam projection contacted by any of the cam projections on the resetting bar according to the position of the latter relatively to the fixed cam projection and the direction of adjustment of the carriage.

26. The combination with a totalizer carriage; a series of totalizer wheels mounted therein; a series of actuators relatively to which the carrlage and totalizer wheels are transversely adjustable in either of two directions; and carrying mechanism for the totalizers, including individual transfer elements adjustable with the carriage; of drive means for the transfer elements, relatively to which the transfer elements are adjustable; 9. universal resetting member shiftable with the carriage and having a series of spaced cam V projections; and a stationary cam lying in the path of the cam projections on the resetting member, and effective to cause the operation of the resetting member incident to the shifting of the totalizer carriage.

27. In a transfer mechanism, the combination with totalizer wheels; actuators therefor; a trans- U fer pawl; and means to advance and retract the pawl; of a combined guiding and shifting means for the pawl; a switch member operable at a predetermined time in the rotation of a wheel of lower order; and a transmitting element ac- 0d tuated by the switch member to operate the combined guiding and shifting means to positively place the pawl in effective position relatively to a wheel of higher order.

28. In a transfer mechanism, the combination with totalizer wheels; actuators therefor; a transfer pawl; and means to advance and retract the pawl; of shiftable means to guide the pawl; a switch member operable by a wheel of lower order at a predetermined point in its rotation; and a transmitting element actuated by the switch member to positively shift the guide means and pawl to locate the pawl in effective position relatively to the wheel of higher order, the transmitting element adapted for movement relatively to the switch member and the guide means.

29. In a transfer mechanismjthe combination with totalizer wheels; actuators relatively to which the wheels are shifted into and out of engagement; a transfer pawl for a wheel of higher order; means to advance and retract the pawl; and means to guide the pawl; of a switch member operable by a wheel of lower order at a predetermined point in its rotation; and a transmitting element actuated by the switch member, and engageable thereby in either position of the totalizer wheels relatively to their actuators, to shift the guide means which operates upon the pawl, to place the latter in effective position relatively to the wheel of higher order.

30. The combination with actuators; and a carrying mechanism of a series of totalizer wheels shiftable alternately into effective position relatively to the actuators and the carrying mechanism, respectively; the carrying mechanism in-- cluding a normally ineffective transfer pawl operable to turn a wheel of higher denomination; and means to actuate the pawl; of a switch member shiftable with the totalizer wheels and adapted to maintain control of the carrying mechanism when the totalizer is in either of its positions, and operable by a totalizer wheel of lower order at a predetermined point in its rotation; and means interposed between the switch member and the transfer pawl, and operable by the switch member, to positively shift the transfer pawl to effective position.

31. The combination with a plurality of totalizer wheels; actuators therefor and relatively to which the wheels are engageable and disengageable; a transfer pawl to coact with a wheel of higher order; and means to drive the pawl; of a guide member for the pawl shiftable to one position or another to render the pawl effective or ineffective; a pivoted switch shiftable with the totalizer in its engagement with and disengagement from the actuators, and operable by a wheel of lower order at a predetermined point in its rotation; and means operable by the switch member and constantly engaged thereby to shift the guide member and locate the transfer pawl in one of its positions.

32. The combination with a set of actuators; totalizer wheels shiftable to engage and disengage the actuators; a transfer pawl for one of the wheels; and means to drive the pawl; of a shiftable guide to direct the pawl; a switch member shiftable with the totalizer wheels as they engage with and disengage from their actuators; an interponent between the switch member and guide; and an extended contact formed between the switch member and interponent to enable the switch member to control the interponent in either position of the totalizer wheels relatively to their actuators.

33. In a transfer mechanism, the combination with totalizer wheels; actuators therefor; a transfer pawl; and means to advance and retract the pawl; of a switch member operable by a wheel of lower order at a predetermined point in its rotation; a transmitting element actuated by the switch member when thus shifted; a guide in the path of the transmitting element, to be shifted thereby; the guide connected with the transfer pawl to shift the latter from its ineffective to its effective position relatively to a wheel of higher order; and means to automatically restore the pawl to its ineffective position, and through the pawl, to return the guide, the transmitting element and the switch member to their normal set positions.

34. In a transfer mechanism, the combination with totalizer wheels; carrying mechanism therefor, including a transfer pawl; shiftable into and out of effective position relatively to a wheel of higher order; and means to advance and retract the pawl; of a shiftable positioning means for the transfer element; means coacting with the positioning means to retain the transfer pawl in either of its positions; a switch member operable by a wheel of lower order at a predetermined point in its rotation; an l a transmitting element loosely mounted between the positioning means and the switch member and with which the switch member contacts to shift the positioning member and pawl to render the pawl effective.

35. The combination with a plurality of totalizer wheels; actuators therefor; a transfer pawl to coact with a wheel of higher order; means to drive the pawl; and a guide member for the pawl shiftable to one position or another, to render the pawl effective, orineifective; of means to yieldingly retain the guide member in, and complete its movement to, either of its positions; a switch member operable by a wheel of lower order at a predetermined point in its rotation; and means operable by the switch member, and relatively to which the guide member is shiftable, to positively switch the guide and pawl to one of its positions.

36. The combination with a plurality of totalizer wheels; actuators therefor; a transfer pawl to coact with a wheel of higher order; means to drive the pawl; and a guide member for the pawl shiftable to one position or another, to render the pawl effective, or ineffective; of a springactuated beveled latch, and a rib, relatively cooperable to complete the shift of the guide member; a switch member operable by a wheel of lower order at a predetermined point in its rotation; and means operable by the switch member, and interposed between the switch member and the guide member, to switch the guide member and pawl to locate the latter in its effective position.

37. In a transfer mechanism, the combination with totalizer wheels; a transfer pawl for a wheel of higher order; and means to drive the pawl; of a rocking guide for the pawl; a switch member operable by a wheel of lower order at a predetermined point in its rotation; and a transmitting element reciprocable tangentially relatively, to the path of travel of the rocking guide, and actuated in opposite directions by the switch member, and by the rocking guide, respectively.

38. In a transfer mechanism the combination with totalizer wheels; a normally ineffective transfer pawl for one of the wheels; and means to drive the pawl; of a shiftable guide for the pawl; a switch member operable by a wheel of lower order at a predetermined point in its rotation; and a member interposed between the guide and the switch member, and actuated in one direction by the switch member to shift the guide to locate the pawl in its effective position, the pawl, incident to its operation of its totalizer wheel, adapted to return the guide, the interposed member and the switch member to their normal positions.

OSCAR J. SUNDSTRAND. 

